Variable delivery pressure fluid engine



Oct. 13, 1959 J. w. Housr-:R

VARIABLE DELIVERY PRESSURE FLUID ENGINE oct. 13, 1959 1w. Housl-:R l2,908,224

VARIABLE DELIVERY PRESSURE FLUID ENGINE V EN TOR.

Fq BY use-.R

Oct. 13, 1959 J. w. HousER 2,908,224

VARIABLE DELIVERY PRESSURE FLUID ENGINE `Filed Aug. 20. 1954 8sheets-sheet :s

INVENToR. .7b/m N. Hause/e l BY @g1/Qn...

oct; 13, lss

J. w. HOUSE-R l2,908,224

. VARIABLE DELIVERY PRESSURE FLUID ENGINE I vFiled Ag) 2o. 1954 8Sheetrs--Sheet 4 7 Tan/IE vs Oct. 13, 1959 l J. w. HousER VARIABLElIADIEILIVERY FLUID, ENGINE Filed Aug. 2o. 1954 `:a sneet-sneet 5unrl'lllllllA ,Y JNVENToR. v J'OHNJV. Housk AT -ra Ng y:

Oct.fl3, 1959 J. w. HoUsER VARIABLE DELIVERY PRESSURE FLUID ENGINE FiledAug. 2o. A1954 8 Sheets-Sheet 6 1959 l J. w. HouvsER 2,908,224

VARIABLE DELIVERY PRESSURE FLUID ENGINE l v Filed Aug. 2o. 1954 u Oct.13,

- 8 Sheets-Sheet 7 oct. .13, 1959 J. W. HOUSER VARIABLE DELIVERYPRESSURE FLUID ENGINE Filed Aug. 2o. 1954 8 Sheets-Sheet 8 INVENTOR.Jaan YW, )logge/e i rroeucys United States Patet O VARIABLE DELIVERYPRESSURE FLUID ENGINE .lohn W. Houser, Willow Grove, Pa.

Application August 20, 1954, Serial No. 451,323

18 Claims. (Cl. 103-120) (Granted under Title 35, U.S. Code (1952), sec.266) The invention described herein may be manufactured and used by orfor the Government of the United States of America for governmentalpurposes without the vpayment of any royalties thereon or therefor.

The present invention pertains to the art of pressure fluid engines,which includes the art of pumps, and the invention is particularlyadapted for use in power pumps.

A pressure uid engine that embodies the invention comprises `a set ofcircular panels that are positioned faceto-face and spaced apart, andare rotatable in unison on axes that intersect. The face of each paneldenes a plane, and the axis of rotation for each panel is concentricwith and normal to the plane of its face. The space between opposedfaces of the panels is enclosed in a container that extends around theperipheries of the panels. A plurality of partitions between opposedfaces of the adjacent panels extend radially to the container, and theydivide the space between opposed panel faces into a set of workingchambers arranged circumferentially.

The angle between the axes of the several panels is variable, and thisvaries the angle between opposed faces of the panels. By the panelsrotating in unison with opposed faces out of parallel relationship, apoint on one face moves towards and away from its corresponding oppositepoint on the opposed face, once during each revolution, and volumetricvalues of the several working chambers are varied accordingly. Theseveral working chambers in succession circumferentially pass eachthrough a cycle of volumetric changes from a minimum to a maximum andback to a minimum, the complete cycle being a revolution.

An inlet port and an outlet port communicate with the several workingchambers in succession, and are spaced apart circumferentially. One portis located where volurnes of the chambers are in process of increasing,and the other where the volumes are diminishing.

For the pressure fluid engine to operate as a power pump, its exhaust isconnected to a power system that demands lluid under pressure to performits work. For example, the power system may include a fluid motoroperable to raise or lower the landing wheels of an aircraft. Theexhaust of the power pump is connected internally of the engine, througha suitable fluid passage or manifold, with the outlet port, which islocated where volumetric values of the working chambers are decreasing.The intake of the pump is connected with an external source of fluidunder a lower or nominal pressure, and internally of the engine isconnected, also through a suitable fluid passage or manifold, with theinlet port that is located where volumetric values of the workingchambers increase.

The pressure or power capacity of the pump may be varied in accordancewith variable pressure requirements of the power system in which thepump is to be used. Adjusting mechanism may be provided to control thepressure output as needed progressively between a maximum, which is therated capacity of the pump, and a minimum, which may be as low as nopower output at ICC all. The power capacity of the pump is controlledfor any given service by varying the angular displacement between theaxes ofthe several panels.

When the saxes of the panels are in line with each other, the planes ofopposed faces of adjacent panels are parallel, and rotation produces novolumetric change in the working chambers. Maximum or rated pressureoutput occurs when the axes of the several panels of the set aredisplaced to the maximum extent that the physical structure of theengine permits, which corresponds with maximum angular displacementbetween opposed faces of adjacent panels.

Dimensions of the engine as a power pump are selected for a volumetriccapacity which is determined by the volumetric needs of the power systemthat is to be supplied by the pump. The pressure build-up of the pump,constituting the difference between exhaust pressure and the pressure offluid at the intake, varies inversely with reference to the volumetricdifferential between maximum and minimum volumes of the workingchambers, and is increased particularly by the minimum volume beingdiminished. In addition to dimensions of the pump being sucient for therequired volumetric capacity, a structure is adopted to attain a minimumvolumetric value in the working chambers that is as low as possible,thereby to attain the maximum available pressure build-up.

In the specific structure of the disclosed embodiments, the set ofpanels compn'ses a pair of outboard panels with an inboard panel betweenthem. The outboard panels are secured to each other spaced apart andfaceto-face, with the planes of their several opposed faces heldparallel to each other. By the inboard panel being positioned betweenthe outboard panels, its opposite faces are positioned each opposed tothe inboard face of one of the outboard panels. The disclosed structurethereby constitutes two pump units, located respectively on oppositesides of the inboard panel.

The outboard panels are rotatable on a common axis that passes throughthe centers of the inboard faces of both panels. The inboard panel isrotatable on an axis through its center that intersects the axis of theoutboard panels at a point Inidway between the inboard faces of theoutboard panels.

The structure of the set of panels constituting the several outboard andinboard panels constitutes a rotor that rotates in a stator thatembodies the intake and exhaust, the inlet and outlet ports, and theconnecting passages between the intake and inlet port and between theoutlet port and exhaust.

More detailed understanding of the principles of the invention, anddisclosure of several practical embodiments thereof, are contained inthe accompanying drawings, in which Fig. 1 is a side elevation of apower pump embodying the invention,

2 is a cross-section in plan, taken on line 2 2 of lg- J Fig. 3 is across-sectional elevation, (taken on line 3 3 of Fig. 2,

Fig. 4 is a cross-sectional elevation, taken on line 4-4 of Fig. 3,

Fig. 5 is a fragmentary cross-section similar to Fig. 4, with partsdifferently placed with reference to each other,

Fig. 6 is a cross-section, taken on line 6-6 of Fig. 5,

Fig. 7 is an exploded view with pants in perspective, showing the rotorof the pump in Fig. l,

Fig. 8 is a fragmentary4 cross-section in plan, showing parts of Fig. 2differently placed with reference to each other,

Fig. 9 is an end elevation, viewed from the right of Fig. 8,

Y 3 Fig. is a cross-section, taken on line 10-10 of Fig. 8,

Fig. 11 is a developed viewof the working barrel, viewingrthearrangementofports fromthe exterior, Y

Fig. l12.is'an end 'elevationtofapower pump .comprising anotherembodimentr ofthe invention, Y

Fig-'13 is a crosssectiona1 elevation, .taken on line 13-13of Fig. 12,

.1l-lig. 14,'is aside elevation viewed .from the .left in-Fig. 12, withparts broken away andpartlyA in section, toshow theY interior of thepump withparts located with reference to eachy other diierently than. invFig. 13,

`Fig. 15 -is a Lcross-sectional elevation, taken online 1\s -1s'.0fFig.14, n

16 is an exploded view with parts in perspective, showingthe rotor, p Y

Fig. 17 is anexploded viewwithrparts'in perspective, showingthe shell, Al Y' Figs. 18, j19, '20, and 21 'show face viewsof-,the several parts ofltheV shell, and Y Fig. 22 is a cross-sectional detail, taken on line22-22 of Fig. 15.` Y

Apressure fluid engine embodying. theinvention is disclosed in Figs. lto 11 inclusive, anditcomprises a rotor 1-1, which rotates'insidethestator 12.

Rotor 4111, Figs. 2, 3 and 4,compr1ses `adjacent.circular f panels. 4Inthe disclosed structure, one of theseyeral adjacent panels comprises apair of outboard-,panels 17. and 18,which are held spaced apart.-'I'hezotherfofthe adjacent panels is inboard panel 19, which ispositioned in the space between the pair of outboardpanels v17- and 18,and thereby is positioned adjacent'to panel 17..aft one of 'itsV sidesorl faces, and adjacent to the other outboard panel .18 at its otherside. See Fig. 7 also.

Outboard panel 1'8 comprises an .inboardface 20 that defines aV plane.Theother outboard. panel 17 also comprises .its inboardtface `22, whichalsodefines a, plane. .Bolts 23 are projected through the outboardpanelsy17 and y18, and each through a spacer member-.infthe'form of-asegment2'4 between they panels, the several spacer members serving toholdi-nboar'd faces 20- and '22 of respective outboard panels .1'8 and\17 face-to-face and their planes inparallel relationship. Shaft.21-is1secured to panel.18,`and is common to-bothoutboard panels-.17.and18,' the axis of the shaft being directed through the cenjters of theoutboard panels and concentrically perpendicular to the planes of theirseveral inboard faces ..20 and 22.

Panel 17 comprises seat 26, Fig. 3, which is recessed `into face`22 andis contoured spherical. -Face .20 of .panel 1'8 similarly comprises therecess of sphericalseat V27, the

several-seats 26 and 27 being contoured spherical continuously on acenter located on the axis.v of vshaft .21- at the midpoint between theplanes of inboard faces 22 and 20 when panel17 is secured to panel 18 asdescribed by means of bolts 23. The inner edges of spacermembers24 arecontoured spherical to seat against spheroid 28. Y Seats 26 and 27, andspacer members 24 between thern,-con Astitute a spherical bearingsurface or socket that contains spheroid 28. Shaft 29 is secured tospheroid.28,-..and.is yprojected through the aperture of panel 17-thatjncludes seat 26. The axis of shaft 29 is directed through thevcenter of spheroid .28, where it. intersects fthe axis ofrshaft, 21 ata point midway between inboard faces 20 andz22gof ,respective outboardpanels 18 and 17. See Fig. 7 lalso.

The aperture of panel 17 is bevelled at 30, Eig .3,rand shaft429-comprises the.annularvundercutv-Sl adjacent to lsph/eroid .28. .See Fig.2. Shaft 29 can be displaced angularly lwith reference toshaft 21 byspheroid28being rotated in the socket of-.seats -26 and.27, the,magnitude of angular displacementV being. limited by undercut 31.vofshaft 29 engaging bevel 30 of panel 17, as seen in Fig. 6. Inboard panel19 is secured to ysphe'roid 28-.as vseenin Fig. 7, with its center-planeperpendicular to fthe axisof .shaft 29, and comprises `opposite faces 36and 3'? .definingparalliel planes which are disposed symmetrically yon24 opposite sides of the center-plane of panel 19. Inboard panel 19positioned between parallel outboard panels '117 and 18 locates panels19 an'd 17 adjacent to each other with their respective faces 36 and 22opposed to each other, and locates panels `19 and 18 adjacent to eachother With their respective faces 37 and 20 opposed to each othersimilarly. This provides spaces respectively at the left and .rightofinboard panel 19 in Fig. 2, and respectively betweenV adjacent panels18 and Y19 andbetween adjacent panels 19 and1:7,.constituting,pumpfunits ofthe pressure fluid engine on respectiveopposite sides of the inboard panels. The centerof center-planeet-circularlinboard panel `19 is locatedcoincident withthecenter ofspheroid 28, which coincides with the Apoint of intersection between'theseveral axes offshats `'21 Yand 29.

When shaft 29 is positioned coaxially in line with shaft 21, planes ofrespective opposite faces 36 and 37 of inboardpanel 19 are positionedparallel with opposed face 22 ofpaneli1'7 and opposed face `20:of"panel="18. wWhen shaft'29` is displaced angularly with reference toshaft 21, opposed faces of the severalpurnp unitsjat the'left and rightof inboard panel 19,'betweenfopposed faces y20 and 37 of respectiveadjacentpanels 18and 19, and between opposed faces'36 and 22 o'frespective adjacentpanels l19 and 17, lare-'displaced angularly. withreference to'each other. The angles between opposed faces are equal, andare oppositely directed, as seen inFigsf-Z and6.

Inboard Vpanel- '19 .comprises the radially ldirected notches 32,Figf7,of which there are-'fourin'the disclosedv embodiment, .and 4these arespaced equi-distant circumferentially. Each notch containsV one 'of' thevspacer members24. Each of the spacer members or segments 24 extends. inopposite directions awayV from thel opposite faces 36 and: 37,.of1inboard,panel19, and into abutting engagementpatits respectiveopposite ends'with faces '22 and 20 of respective -panels 17 and 18."The several spacenmembers'24 are directed perpendicular tosthe planesofthe several faces '22. ofpanel 17, and"20 of panell-S. The angle. ofeach spacer member 24 relative .to oppositefaces .36 .and 37Vofinboardpan`ell19 varies duringrotation of rotor.11.of the severalaxes of the .singularly-displaced shafts 29 .and`21,'there" being acomplete cycle of angular. ,changes between Y panel ".19 andspacermembers 24.during. each revolution ofthe rotor.

,Each spacer-member124.extendsfrom its concavely VYspherical surface.that v.fits andbears against 'the surface. of `spheroid.28 .to vthe.perip,heries of panels '18, 19 and 17. vEach spacer memberV 24 liesinaplane vthat is fa radial .planeof theassembly.. constituting the pairof outboardpanels 18 and :1`7.and,.thc several spacer members therebyform each a partition. The several partitions. of spacer-members...24.divide, the spaces,V between opposed-.faces .36 and y.22.of `respective adjacent panels 19.-.and17, ,and between `\-opposed faces37 and 20 of Vrespecz-tive 5adjacentpanels.19.ax1d118, .in each caseinto four working barrels .distributedcircumferentially. Eachoffthe'pump units, .respectively at the. left and right of..inboard-.panel 119V Vin V1`f`ig.."2,.. consists fof four working.chambers, each .defined circumferentially .byY two adjacent spacerlmembers,lorfpartitions .24. .The pump characteristics =of. the severalpump units are same same,:and .each lsupplies-halfofthetotalsvolumetric. capacity of lthe engine.

EachY of ythe notches v 32,"Fig."7, -isz contoured cylindrical onza.radially `directed axis through fthe 'center` offspheroid .'28, andconstitutes. a `bearing for'tagpin `3r3-tofIotate on its. axis. .Eachpin 33: comprises its slottconstituting opposite bearing surfacescompanion'ztoopposite Vside surfaces'offits corresponding spacermember-24,4 which slides" relativelylengthwise *of4 itself along-theslot .34. "With Ieach revolution Aof-roto'rI 11 onythe severalaxesof 'the angularly-displaced sharft21and'-29,-each"pin33 fslidesto-aridlfro jvalong *its corresponding-A partition of spacer 24betweenfac'es" 22 and204 of f respective outboard panels 17 and 18.Because rotating inboard panel 19 travels along a path positioned at anangle to outboard panels 17 and 18 rotating in unison therewith, therelative movement of a partition 24 sliding along slot 34 of itscorresponding pin 33 is accompanied by rotation of the pin, which makesa complete oscillation in its bearing 32 in the same time interval of arevolution of rotor 11.

By means of the described structure, parallel outboard panels 17 and 18are keyed to the angularly-displaced inboard panel 19, andthe severalpanels 1S, 19 and 17 rotate in unison to constitute rotor 11, withoutboard and inboard panelsV severally rotating on the axes of theirrespective shafts 21 and 29. Ally of the several working chambers of theengine are closed and sealed from each other by `thedescribed structureof the partitions 24 and their companion pins 33.

By the described operation, any point on the face 36 of inboard panel 19moves towards and away from its correspondingly opposite point onopposed face 22 of outboard panel 17, once in the cycle of a revolutionof rotor 11. Likewise, any point on face 37 of inboard panel 19 movestowards and away from its correspondingly opposite point on face 20 ofoutboard panel 18 in the same time interval. Volumetric values of theworking chambers are varied accordingly. In the cycle of a revolution ofrotor 11, a working chamber changes its volumetric value progressivelyfrom a minimum volume to a maximum volume, and back to the minimumvolume.

The range of volumetric changes is the same in all working chambers. Inthe several pump units at the left and right of the inboard panel 19 inFig. 2, the working chambers pass through their cycles of volumetricchanges in succession circumferentially, according to the direction ofrotation of rotor 11, through alternating half-revolution phases ofincreasing and decreasing volumetric values, the cycles in the two pumpunits being a half revolution out of phase with each other.

Stator 12 comprises housing 16, which contains working barrel in whichthe working chambers of rotor 11 operate. Housing 16 rests on legs 39,Figs. 1, 3 and 4, and comprises the cavity member 4G into which theworking barrel 15 ts and is inserted.

The inside surface of working barrel 15 is contoured concavelyspherical. The outside surface of rotor 11, constituting the peripheraledges of panels 18, 19 and 17 with the outer edge surfaces of segments24 continucus therewith, are contoured convexly to fit in the concavelyspherical working barrel 15, and the rotor rotates therein. Workingbarrel 15 constitutes a container that closes the several workingchambers of rotor 11 peripherally.

Working barrel 15 consists of two hemispherical half members, 41 and 42,Figs. 2 and 3. Half member 41 is inserted into the cavity of member 40rst. Rotor 11 then is inserted, and half member 42 follows to containthe rotor. Closure member 43 of housing 16 then is positioned againstcavity member 40, and is secured in place by means of cap screws 44.

Cavity member 40 is extended to include the bearing 45 for shaft 21 ofoutboard panels 17 and 18. In the disclosed structure, shaft `21 ishollow, and drive shaft 46 is keyed thereto at 47. Rotor 11 is rotatedinside working barrel 15 by drive shaft 46 being driven from anysuitable power source, not shown. Packing 48 to conne lubricant istightened around drive shaft 46 by means of packing closure 49 andscrews 50, Fig. 2.

Shaft 29 is contained in sleeve 52 that embodies the bearing 53 for theshaft. Sleeve S2 comprises a head, the surface 54 of lwhich is convexlyspherical. Con- Vcavely spherical surface 55 of half member 42 iscompanion to and bears against the convex surface 54 of sleeve :52. Thehalf member 42 comprises the convexly spherical surface 56 also, whichis concentric with surface 55, and which is companion to andbearsagainst the concavely spherical surface 58 of nut 57. Nut 57 isthreaded onto sleeve 52, and holds companion surfaces 54 and 55, ofsleeve 52 and half member 52 respectively, in correct bearingengagement, as also companion surfaces 56 and 58 of half member 42 andnut 57 respectively. Lock nut 59 holds nut 57 secure.

Bearing surfaces 55 and 56 of half member 42 form a dome which comprisesaperture 6i) through which sleeve 52 containing shaft 29 projects.Aperture 60 is a slot, and it is extended horizontally to a length thatenables shaft 29 to be displaced angularly with reference to shaft 21 tothe maximum desired extent as determined by undercut 31 of shaft 29engaging bevel 30 of panel 17, as seen in Fig. 6. The width of slot 60is determined to engage sleeve 52 and form a guideway for shaft 29during its angular displacement with reference to shaft 2,1. See Fig. 9also.

Closure member `43 of housing 16 comprises the bearings 62 and 63 forrespective opposite ends of traverse screw 64, on which traverse nut 65is threaded. Traverse screw 64 comprises the squared end 66 that extendsto the outside of closure member 43 to receive a suitable wrench, notshown,` and by means of which screw `(4 is rotated to traverse nut 65along its length.

Closure member 43 'comprises nut 68 for coniining lubricant, which canbe removed to inspect and service bearing 62 at one end of traversescrew 64. Bearing 63 at the opposite end of traverse screw 64 may beinspected and serv-iced by 'removing nut 69. Packing 70 in nut 69contines lubricant at the other end of screw 64, and is tightened aroundscrew 64 by means of packing nut 71.

Sleeve 52 comprises the ears 73 that project away from its end tostraddle and engage traverse nut 65 as seen in Figs. 2, 8 and 9. Ears'73 comprise notches '74, which are engaged by respective pins 75projected oppositelyfrom nut'65. When traverse screw 64 is rotated bymeans of 4a wrench applied to squared end 66, nut `65 is traversed alongthe screw, thereby displacing shaft 29 to vary the angle between theaxes of shafts 21 and'29 as desired. The angle between inboard panel 19and the several parallel panels 17 and l18 is varied thereby to adjustthe pressure output of the engine operating as a pump. Figs. 2 and 6'illustrate the adjustment of maximum pressure capacity.

As a power pump, the pressure fluid engine of the present inventionreceives fluid through intake 7'7 from any suitable source of fluidunder relatively low or nominal pressure. Operation of the pump is tosubject this iiuid to a higher working pressure, and to feed it inpressurized condition to a power system that requires pressurized fluidfor its operation under the working pressure of the pump. By way ofspeciic example, the pumpy of the present invention may be used to diiveone or more pressure iluid motors.

Intake 77 and exhaust 78 are standard pipe connections, and are alike.The =whole engine is symmetrically the same on opposite sides of itscenter, enabling rotor 11 to be driven alternatively in either ofopposite directions depending upon the needs of a given installation,connections 77 and '78 to be used interchangeably for intake or exhaust,and power output to be adjusted, from no pressure differential betweenexhaust and intake coincident 'with shaft 29 being coaxially in linewith shaft 21, to the desired pressure output by nut 65 being traversedalong screw 64 in the appropriate of alternative directions in either ofopposite directions.

Connection 77 is designated the intake by way of assumption as a meansto make clear the pump characteristics of the engine, and rotor 11 isdriven in the counterclockwise direction when viewed from the left inFigs. 2 and?. 'Rotation is clockwise in Figs. 4 and 5. Connection 78 isthe exhaust. This means, with reference to Fig. 2, that rotor'..moving'm its `upwardly direction on the near or viewer .sideoftheiigure, and is mow ingdownwardly on the .remote-orhidden side,ythisbeing soof both pump units :atthe left and .rightrespectively ofinboard panel;19

Of the .pump unit ,at :the leftf inboard panel 19 `in Fig. 2,itwillebeobser'ved that working lchambers are the increasing phase ofthe .cycle .of their -Jvolumetric changes on. the :near side, andon.thezremotegsidezthe Working chambersof the sameepumpunit are in.theydecreasing phase of vtheir volumetric changes. Inthe pump unit atthe .right of inboardpanel 19, .working chambers are vin :their.increasing V.phase of vvolumetric changes on the remote.side,;andzareinftheirdiminishingphaseron the near or. viewers side. Thisis.coincidentalwiththetwo pump units being '180V :out-of phase with..each other, as explained Vhereinbefore.

Each pumpunitlhas aninletport, and anzoutletport, and these in thedisclosed embodiment, are ingtheworking barrel 15. Inthe'pumpiunitatstheleft of inboardpanel .19 in.Fig. 2, ..and.\also in :Fig 3,-the-inlet port 80 is at the topinFig. 3, .and thesoutlct port8,1.'isat.thelbottom. The inlet port;8-3.of.the.pump.unit at.the.rightis atthe bottom in Fig. 3, vand the.outlet.portf82 is :atlthe top. lForthe .pump .unit atthe left ofinboard .panel .19 in Fig. 3, inletand=outlet ports 80 and 8.1 .respectively are in the half.member..41v of.working barrel :15, andoutlet andinletports182.and 83 respectively. ofthe4 pump. unit at the right are in half member 42. SeefFfig. .ll also.

The manifold structure` of lthe presently.` considered engine isembodied in workingbarrel :15, and. is': illustrated in Fig.llwwhichviews the outenperipheryoftheworkingbarrel developed.Annularpassage .84,.onstrituting a channel along the peripheral surfaceof half member. 41,

`half member 42,- a Asimilar annular; channel i90 -extends .fromrinlet-portfSS-to cross passage 91,.which..is.con rtinuous-1withcrosspassagewSS along vtheperipheral sur- 'face of working barrel `15,.at a positionwheredntake- 77 is located. Fluid received throughintaker77-is distributed .inopposite directions along annular-passages84 and .9.0 to the working -chambers of thepump vvunits.-at.the left andright respectively of` inboard panel .19.i.nvFi.gs. .2. and 3, throughtheir respective` inlet ports l.80.andf 83.

Similarly, annular passage 86 along-the peripheral surfaceofhalf-member41, and the similar annular-passage 88 of half member 42,connect 1 their respectiveoutlet ports-'81- and 82 with theirrespectivecrosskpassages 87 and- 89, which arecontinuouswith eachother along. thenperipheral surface of working barrel L15, and are` located at theexhaust 78. Fluidthat-hasbeen.pressurized in the several-pump unitsatltheleft `andright of-inboard panel 1-9 in Figs. 2 and 3-is drivenout. of their Vrespective outlet lports181 andf82,-andvthroughtheir.respective `annular Ypassages-86 .and 88, totheexhaust 78, whichA delivers the- `lluidV underV pressure.

Fig. discloses the pumping action of thelpumpf-unit at vthe left-ofinboardpanel 1-9 in Figs. Zand-3, andhillustrates thevalVing-actionby the inletand outletportsgS.) and Slrespectively,operating on the Aseveral lworking chambers as. they pass infsuccession.

The workingV chamber at the uppermost posit-ion inFig. 5,extending-'between adjacentpartitions 24, is intheprocess of-Aincreasing its yolume,and it istakng'in--uid V`vfrom Vintale7-7 `throughVits 'inlet port 80. Theworking chamber atf the lowermost'positioninthe-gure is-dim-inishing its..volumetric value, andI is `dischargingthef'fluid it VhasY subjected-torpressurethrough the outlet port 81,which uidinpressurized Y condition -is 'driven out of exhaust 78.

With reference to; the working chambers at-the--rightrand left inFig.-5, -it-will-be-observed `that-eachH of these is `completely closed.Clockwise rotationbeing assumed, 'the trailing-' partitionf'24 of each,l-upperat -theright` and 'lower at the-leftyhasA justmoved beyondya-port, these?,`

extendsfrom the inlet-port `80 tocross-.passage 1.85. In ,35

8 beingtinlet port80-,in the case oftheworking chamber at theright, and.outle t,port8 l.in thecase ofthe working chamberjattheleft. Q the sametime, theleading partition 2,410f ,eachoflthesejworkingchambers ismoving into -positionto.openits- -neXt port, these being outletport 81in thecase ofthelworkingchamber at thev right, andin the casebf theWorking chamber at the left .theinlet port 80. f

I n the pump. iunitat ,the right,of,inboard vpanel 19 in Figs. 2. an d3, the `structure islsymmetrically ,the same as at the left, excepcthatthe inlet.. port ,is at the rlowermost position. in the engine, andtheoutlet `port is at the uppermost. position. .See Pig.. 1 1. All Ytheports, ,8 0, 8d, .82, and :8 3, are the same length andextend `to likeaigularydistances; also all dis ta.nces between nearends ofadjacentports,circumferentiallyare -the same. In the several pump unitsat the ,leftv audrghtQ-inbOard panel 1 9, Fig. 3, adjacentports intheadjaccnt half members ,.41 and 42, consisting,V of the inlet ,andoutletports 80 Aand .8 2 respectively, .and ythe inlet and otulet ,ports81 and 83 respectivelyfare,coextensive circumferentially. The valvingaction of .the inlet and outlet ports .in both pumping unitsis,the same, andas described hereinbefore.

In ,the positionof `rotor 41 1 seenin Fig- 4, there are two.circumferentially ladjacent,working chambers that are receiving'lluidthroughinlet port 8 0, andthese are inthe phase of volumetric inclffeasei The other two working chambers are opento outlet port 8 1, andlfe intheir phase of volumetric decrease. This vcond v ion continues duringthe succeeding 45 angle of rotation ofV rotor 1 1, untilthe positionpfFig. 5 is reached. Nou/,twoofthe four .workingchambers areCompletelyclosed, andlhey continue to be `.c losecl vduring a diminutiveportion only Qfaomplete .revolutionf rotor ,11. A workingshamberremains. closednly,longenough.topreventvidow through .t he workingchamber as a passage f roma highpressure port 1.81l or8.2.tothe.respetivelowfpressure yport 83'are determined accordingly.

1n Eig. 2, rthe .Working chambers are closed at their uppcrmOStand,lowermgstrcsitionsin the .figure And these are Athe positionsofldirection change of changing volumetric values; In thepump units Aatthe left and right of inboard panel 19 in.E ig. 2 ,.direct ion cl 1 a nge to- .wardsand away from absolute. maximum .is attheyppermost andlowermost positions respectively,. and .direction change towards vand.away fromabsolute minimum is at the lowermost anduppermost positionsrespectively.

#It will beobservjed in Eig. 2, that travel 'of inboard panel 19awaygfrom surface 22 ofoutboardpanel 17 towards surface20 ofoutboardpanel 1.8 andback towards 'surfae; 2, 2, once; during cachrevolution'ofrotor..11, is at a'lesser rate with reference to theuniform rate of angular displacementnear theuppermost and lowermost,positions lar displacement ofgits completecycle, andthelpressure changeof uid'inside a closed working chamber is insuflicient to be critical.'A'pressure' chamber in its vphase `of'volumetric increase '.isdrawingiluid through-its inlet port 80 or 83 from intake 77 during virtually acomplete halffrevolution, and during virtually the entireothenhalfrevolution, constituting its phase of volumetric decrease,

-the workingchamber ispouring pressuriz'eduid to exhaust 7 8' throughitsk outlet port 81 or 82.

As has Ybeen observed hereinbefore, the-power capacity ofthe .engine asapump is determined by-the vpressure build-upin the pump,y constitutingVthe pressureldiffer- .ential-between--theexhaust and intake,` =-78Vand77 re- .spectively, -varies inversely `.with :the maximumfandminimum volumes. VYattained. by.'v the @severalnworking chama-bers. :Toattain@ a .pressurezbuild-.up thatisrelatively '-hi`grh,--a.minimumvolumetric `value.iszdesiredthats as low as possible. VFor this purpose,faces 22 and 20 of respective outboard panels 17 and 18 are madefrusta-conical, and opposite faces 36 and 37 of inboard panel 19 alsoare made frusto-conical. This is seen in Fig. 6, as also in Figs. 2 and3.

The conical angle of the several faces 22 and 20 of respective outboardpanels 17 and 18 is the same, and the conical angle of opposite faces 36and 37 of inboard panel 19 are the same. At theadjustment of'maximum orrated power output of the pump, determined by the position of traversenut 65 along screw 64 that is seen in Fig. 2, when undercut 31 of shaft29 abuts against bevel 30 of panel 17 as seen in Fig. 6, the opposedfaces 20 and 37 of respective panels 18 and 19, as also opposed faces 36and 22 of respective panels 19 and 17, are closely adjacent to eachother and parallel at circumferential positions of minimum volume, whichare opposite each other in a diametrical plane. This is so of the pumpunit at the left of inboard panel 19 at the lowennost position in Fig.6, and at the uppermost position in the pump unit at the right. Rotor 11is constructed for face 37 of inboard panel 19 to approach its opposedface 20 of outboard panel 18 as near as possible without touching, andsimilarly for face 36 of panel 19 to approach its opposed face 22 ofpanel 17 as near as possible without touching.

None of the faces 20, 37, 36 andv 22 of several panels 18, 19 and 17describes a plane. Each defines a plane at the base of its cone, andseveral parallel planes along its conical axis. The ends of thepartition members 24 are bevelled, as seen in Fig. 3, to it the conicalsurfaces 22 and 20 of respective outboard panels 17 and 18.

Attention is directed now to Figs. 4 and 5, and particularly to thebolts 23, which hold rotor 11 in assembled condition. In the case ofeach of two oppositely positioned bolts 23, the bore of spacer member 24through which it passes is enlarged, whereas the bores of the other twopartition members 24 are sized to lit their bolts 23. This structureenables those alternate partition members 24 which have the oversizedbores to move circumferential relative to their respective bolts 23, andeach lto move individually relative to its next adjacent spacer memberor partition on both sides. This causes volumetric changes in theworking chambers in response to relative circumferentially movementbetween their containing partitions 24, but these volumetric changes areslight and have no appreciable practical effect on the pumpingcharacteristics of the engine.

Freedom of relative circumferential movement between `adjacent spacermember 24 is provided for operability of the engine, and this is enabledby the oversized bores in alternate partition members. Otherwise rotor11 would be caused to bind, and its rotation would be prevented. Thedescribed relative circumferential movement between next adjacent spacermembers 24 is a mechanical peculiarity of the engine, yfor which thedescribed freedom is provided consisting of next adjacent spacer membersbeing movable relatively towards and away from each other. In theembodiment of Figs. l to ll inclusive, the described oversized boltholes for bolts 23 is the means that is provided for the purpose.

To understand the need, consider a peripheral point on inboard panel 19that coincides with the axis of a radial pin 33. Near the panels 17 and18, the radial distance of this point from the axis of shaft 21 is lessthan at a position midway between the outboard panels 17 and 18 wherethe point crosses the crown of spheroid 28. Therefore, the linear rateof circumferential travel of this point with reference to the axis ofshaft 21 is less near the panels 17 and 18. As each such peripheralpoint on the axis of a pin 33 approaches towards either face 22 or 20 ofrespective outboard panels 17 and 18, its linear rate of travelcircumferentially with reference to the axis of shaft 21 diminishes, andthe rate increases progressively as the point moves away from eitherface Z2 or 20 of respective panels 17 and 18 towards the Y 10 crown ofspheroid 28, where its linear rate of travel is As the result of thedescribed deceleration and acceleration, a pin 33 and its correspondingsegment 24 alternately approaches the next trailing segmentcircumferentially while it recedes from its next segment in ad- Vance,and recedes from its next trailing segment while it approaches its nextpreceding segment. This circumferential movement of a spacer member 24relative to its neighbor is coordinated with its lengthwise travel inbearing slot 34 of its corresponding radial pin 33, and with the pinrotating on its axis.

In the structure of the embodiment of Figs. l to l1, the opposite bolts23 of closely fitting bores of their spacer members 24 as seen in Figs.4 and 5 are tightened to secure the assembly of rotor 11 rigidly andhold outboard panels 17 and 18 rigidly parallel. The other two oppositebolts 23 in oversized bores of spacer members 24 are secured lesstightly to permit movement of their spacer members 24 circumferentiallyto whatever extent is needed to accommodate the described relativecircumferential displacement between adjacent partitions 24.

Another and different embodiment of the invention is disclosed in Figs.l2 to 22 inclusive. lIts principles are the same as already described.In the modiiied structure, rotor 9S, Figs. 13 and 14, rotates in stator96.

Stator 96 constitutes a housing consisting of two half members 97 and98, which are secured to each other along their mid-plane iianges 99 bymeans of bolts 100. Half member 97 comprises a bracket 101, by means ofwhich the engine can be secured to a support, and which may embody anysuitable structure to adapt the bracket to the given standard of 4thesupport. l Shaft 103 is rotatable in the bearing 104 of half member 97,and at its other end in bearing 105 of half member 98. A keying device106 of shaft 103 enables a driving shaft to be attached, the drivingshaft being not shown, by means of which rotor 95 is rotated from anysuitable power source, not shown.l Ball bearing 107 is provided to holdshaft 103 against lengthwise travel in its bearings 104 and 105, andoperates to inhibit chatter at high-speed rotation.

Cylinder 108 is secured to half members 97 and 98, by means of caplscrews 109. Cylinder 108 contains pistons 110 and 111, which are backedboth by a pressure fluid supplied through respective connections 112 and113 from a suitable source, and under control of suitable valvemechanism, which is not shown.

Pistons 110 and 111 are positioned at respective opposite ends ofcylinder 108 in opposed relationship, with roller follower 114 betweentheir heads. A pressure differential between the lluids behind theseveral pistons 110 and 111 operates to actuate the pistons along thecylinder 108 in the direction away from the higher pressure, andfollower roller 114, with arm 115 that carries the roller, is movedaccordingly away from. its mid-position. In the practical application ofthe invention disclosed in the embodiment of Figs. l2 to 22, the valvemechanism is operable alternatively to a higher pressure behind piston111 or to a balance of pressure -behind the two pistons 110 and 111.vAccordingly, by

means of higher pressure behind piston 111 arm 115 is actuated to theleft into the position seen in Fig. 13, or alternatively 'arm 115 isreturned to the right into its mid-position seen in Fig. 14, where it ispositioned and held by a balance of pressure `differential behind theseveral pistons 110 and 111.

The housing of half members 97 and 98 is sealed to confine a fluidlubricant, which can be supplied through the apertures of plugs 116.Packing ring 118 seals the housing 97, 98 at bearing 104, and is heldin' place by retaining plate 119, which is secured by means of capscrews 120. Nut 121 secures shaft 103 to ball bearing 107, and is heldby lock Washer 122. Closure plate 123,

.aeesaae seemed `by eee Serewe -,1.2fl .eal e the-bewies 17h28rnerribers,and.bolts 13S't'hat assemblethe'container and seeure' .theeutbeed Penelmembefs and Spacer fing te veach other. Panel 132 comprisesseat .13 6,`which .is'convlavely'spherical to llit spheroid .1.26, andpanel 133 vsimilarly comprises the concavely spherical seat 137, `whichis'continuouswithseat and with it forms a socket or bearing for thespheroid 1126, 4enabling container 131 :to

be Yrotated `on 'the center of the spheroid.

Panel 132 comprises the face 138, which is Vpositioned opposedto`theface 1729er inboard panel l12S. Similarly, panel fleemprises .feee139, .Wheh .1S Ypositioned Qppoed Ato face 13tloflinboard panel 128.VSee Fig. 16Y also. The space between r-opposed `faces 138 and 17729 ofrespective eutbeetrd and inboard Panels .13.2 and 12.8, and the Spacebetween Opposed .fates 1.3.0 and 139 Of respeetlve .inbeard and outboardpanels 128 and 133, constitute each a pump unit to the leftand rightrespectively of inboard panel .12.8 in Else. f1.3 vand 14, eeehrtlrnplmit .Supplying halfbf the v.total volumetric capacity of `the pressureilu-,id engine constituting the embodiment of Figs. 41 2.to 22.

Arm v1 15, Aimpelled to the left or right. alternatively -by operationof pistons 1.10l and 111 inthe manner described ,herenbefere and.operating ,through e ettuetllre t be 51escijibed hereinafter, displacescontainer131 vangnlarly. on the center of spheroid 1 2 6as a bearing tothe positions .of Figs. 13 and 14 alternatively. In the position.ofrlig. lathe axis .of Container Y131 has .been .displaced 1912.111angle .through the .Center 0f .Sphereid 1.26 with .referente to the axisof shaft 103. Opposed ,faces 138 and 129 of Irespective outboard andvinboard panels 1 -32'and 128 thereby have been displaced angularly, asalso opposed faces 130 and 139 of respective inboard `and outboardpanels 1528 and 133. vThe angles betweenopposed faces 138 and 129, andbetween opposed f aces7 1 3 0\y and 1,379, are the same but oppositelydirected.

By .its movement when actuated by pistons 110 and 111 as described, arm,115 travels in slot 141 of cylinder 10S, F.igs. 13., 14 and 15, andthismovement is limited byarrn 115 4engaging the end 1142 of slot 141, whichconstitutes .a stop.

Faces 138 and 1,39 of respective outboard panels 13 2 and 133 arecontoured truste-conical, as seen in Figs. A13 .and 1 4. When arm 115abuts against stop 142, at the uppermost position in Fig. '13, in thepump unit at the right of inboardpanel128, face 139 of outboard panel133has1moved to a position closely adjacent to face 130 .oflinboardpanel 128, and in parallel relationshipal ong a .radial plane of shaft1.03. Similarly, .at .the left of inboard panel 5128, face 13 8 ofoutboard panel 132 has moved. to a position closely adjacent to face,129er inboard panel 128 at the lowermost position in .the rieure, .andthe eppesetl feeee are Parallel t0 .eeeh

ether. in .e line along the rediel Plane 0f Shaft 103- The conical angleof fnlsto-conical faces 138 and 139 of respective panels 132 and 133 isestablished accordingly,

dis the'samein the two faces 138 and139.

Inboard panel. 128 comprises radial notches 144, Fig. 1 6, which` areequifdistant circumferentially. Notches 144 .are cylindriea'l, and each'constitutes a bearing for a radial i r 1'1 45, which contains'aV slot146 that ts segment l1""17efor bearing engagement therewith. There .are`'lve radial'notches- 144 in the embodimentof Figs; '12 .to122,

in the. pump unit.

1`2 andgfive companion vp ins 1 45 andsegments 147. The pumpunitoneachof opposite. sides of inboard panel i128 is divided vinto fiveworkingzchambers -distributed circumferentially. .Y l' 1 The inboardface of outboard panel 13,2 .is recessedas seen in Fig. 1 6,toconstitute the frusto-conical face 138 of thepump unit `at-.the .leftof inboard .panel .128 in Figs. 13 .and 14, and zthe inboard `face of,the .other outboardpanel 133 is recessed .similarly .to constitute thefrusta-conical face 139 of the other Vpump unit. Each outboard panel 132and 133 is divided equi-distant .cir- 'cumferentially by veradiallydirected partition .members 148 that project towardseach otheraway from frusto-.conilcal faces 138 ,and 139. The live partitionmembers 148 of each outboard panel 3132 or 133 correspond with eachother in the several outboard panels, andlcorrespondwith the respectivelive segments 147 of inboard panel .ln the radial direction, vthe.severalpartition members 1.48 extend each from lthespherical seat 13.6or 137 to the rim 149 of its panel 13 2 or 133, respectively. In eachoutboard panel132 and 1313, and inrspacer ring 134 between them,opposite faces are parallel andflat. Rims 149. embody Lllat'inboardfaces .of .the .several outboard panels 132Y and .133, each delining Yaplane into which respective faces 1,38 and 139 are recessed. Flat rims{149:bear against respective opposite faces of annular spaeerring 134,and the several panels are held in assemoly by means of bolts 135,`seeFigs.- 13 and 14.

`T he inside annular surfacer150 of spacer ring 134 is contouredconcavely spherical, `andlthe peripheralsurface of inboard panel 128,with pins and segments 147 continuously therewith, are contouredconvexly spherical to Yfit in and bear against the concave vannularsurface 150 of spacer Vring 1134. Inside rims .11.49 of the several out-'board panels 13 2 and 133, surfaces 151 extend to their respective.corresponding surfaces I138 and 139 continue ously with annular surface150 of spacer ring-134, but are'somewhat yoversized for clearance. Theseveral surfaces V151 provide the outer peripheral containing wallsor-partitions for the vseveral working chambers of a pump unit, andinthe several working chambersspheroid 126., ,against which sphericalsurfaces 136 and 137 bear, constitutes the inner containing wallopposite outer surfaces 151.

Opposite faces .129 and 130' of inboard panel 12,8 respectivelyconstitute containing walls or surfaces ofthe working chambers of theseveralpump units, towhich respective faces l138 and 1 39 ofthe severaloutboard panels 132 and 133 are opposite, the several segments 147 alsoconstituting containing walls for the several working chambers,continually with their respective corresponding partition members 148'of the several outboard panels. Withspheroid 1256 and inboard panel 128contained in container 131, the two are keyed to each other to rotate inunison andA constitute rotor 95. Radial pin 153, which projects throughannular ring 134 into bore 155 of one of the segments 1.47, Figs. 13 and14, and is held in placeby transverse locking pin 154, operates to keyoutboard panels 132 and.1 33 to inboard panel 128 for their rotation inunison.

Assuming clockwise rotation of shaft 103 viewed from the left in Fig.13, inV the. pump unit at the right of inboard panel 128 in Fig. 13 theseveral working chambers in succession pass through their phase ofincreasing volumetric Values on the near or viewers side of the gure. Atthe same time, the working chambers of the pump unit atthe left passthroughtheir phase ofl increasing volumetricvalues o n the remote orhidden side of Fig. 13, .and pass through their phase of decreasingvolumetric values on the near or viewers side. The working chambers ofthe pump unit at the right pass. through their phase.. of decreasingvelumetrie. Vvalues on the hidden aident Eig-l3- f AS 4inthe .ease efthe embodiment ef Figs Vl t0 1l, there-is relative .eireumfereatialmovement between ad.-

jacent segments 147 towards and away from each other, and for the samereason. Because container 131 of outboard panels 132 and 133 and inboardpanel 128 rotate in unison on different axes that are angularlydisplaced with reference to each other, the rate of linear travelcircumferentially of a peripheral point on inboard panel 128 thatcoincides with the axis of a pin 145 decreases progressively `as itapproaches an outboard panel 132 or 133, and increases progressively asit recedes away from an outboard panel, due to the radius of this pointvarying constantly in this rotation on the axis of container 131. SeeFig. 13.

In the embodiment of Figs. 1 to 11 as described hereinbefore, and asseen in Figs. 4 and 5, holes for bolts 23 are oversized incircumferentially alternate partitions 24 are to meet the mechanicalpeculiarity of next adjacent partitions oscillating relatively towardsand away from each other in time with the cycle of a revolution. To meetthe same mechanical peculiarity in the embodiment of Figs. l2 to 22,partition members 148 of outboard panels 132 and 133 are narrowercircumferentially than the slots 146 of their corresponding radial pins145 of inboard panel 128, and also narrower than segments 147 which t inthe slots. This permits relative circumferential displacement betweencircumferentially adjacent segments 147, and also between each segment147 and its corresponding partition members 148 of both outboard panels132 and v133, allowing adjacent segments 147 to move relatively towardsand away from each other to the extent that is necessary under thedescribed circumstances. The described structure of only one pin 153keying panel 128 to its container 131, at one point onlycircumferentially, enables the described relative movement between nextadjacent segments 147.

Each partition member 148 of an outboard panel 132 projecting away fromthe frusto-conical face 138 engages its corresponding segment 147 at oneof the end faces thereof, the opposite end face of the segment engagingthe corresponding partition member 148 of the other outboard panel 133in a like manner in the plane of rim 149 thereof. The length of eachsegment 147 corresponds with the thickness of annular spacer. ring 134,and its opposite end faces bear in sliding engagement against respectiveend faces of corresponding partition members 148 lin relativecircumferential displacement.

When the pump is adjusted to the position of Fig. 13 by means of pistons110 and 111, and rotor 95 is rotated under drive of shaft 103, at anyradial pin 145 panel 128 travels in a complete' revolution from adjacentto face 139 of one outboard panel 133 towards and adjacent to face 138of the other outboard panel 132 and back to adjacency with face 139 ofthe first panel 133. Each radial pin 145 slides along its correspondingsegment 147, which is long enough never to come out of engagement withits corresponding slot 146 of pin 145. In the cycle of the samerevolution, each pin 145 also makes one complete oscillation on the axisof its bearing 144 of inboard panel 128, the extent of this rotationbeing determined by the angle of displacement between inboard panel 128and outboard panels 132 and 133 that is determined by the adjustment ofpistons 110 and 111. Also during the cycle of the same revolution ofshaft 103, all segments 147 except the one which is keyed to container131 by means of its pin 153 are displaced circumferentially relative totheir respective corresponding partition members 148 of both outboardpanels 132 and 133, and this enables coincident relative circumferentialmovement between each of next adjacent segments 147.

Each of corresponding partition members 148 in the several outboardpanels 132 and 133, with their corresponding segment 147 between them,constitutes a partition extending through inboard panel 128 which servescorrespondingly opposite working chambers of both engine` units. Thispartition extends from face to face of frusto-conical faces 138 and 139of the several outboard panels 132 and i133, similar to partition 24 inthe embodiment of Figs. 1 to 11. In the case of one or the other of thetwo engine units, a' partition between circumferentially adjacentworking chambers consists of a partition member 148 continuous with itscorresponding segment 147, the length of the partition varying accordingto volumetric changes in the working chambers that it separates. While aface 129 or 130 of inboard panel 128 is moving away from its opposedface 138 or 139 respectively, of respective outboard panels 132 or 133,the partition of partition member 148 increasing in length to compensatefor the added distance 'between the opposed faces, and the correspondingsegment 147 sliding in its slot 146 provides the added length as needed.At the same time, the corresponding partition of the other engine unit,embodying vcorresponding partition member 148, decreases in length, thecompensation for length decrease being provided again by thecorresponding segment 147 sliding along its slot 146.

Bores 157 of the several outboard panels 132 and 133, Figs. 13 and 14,that contain the bolts 135 lie on a circle concentric with container131, and in the rims 149 of the several outboard panels are locatedcircumferentially each about midway between adjacent partition members148 that define the several working chambers circumferentially. Eachbore 157 is counterbored at 158 into the outboard face of its panel 132or 133, to contain the head and nut at respective opposite ends of thebolt 135 embedded Within the exterior contour of rotor 95. Eachcounterbore extends laterally, and also to a depth, to penetrate intoits corresponding working chamber, as seen in Fig. 16, and thusconstitutes a passage for fluid flowing into and out of the workingchamber.

In its phase of increasing volumetric change, a working chamber deinedby adjacent partition members 148 draws fluid into itself through thepassage of its counterbore 158, and it pressurizes the fluid during itsphase of decreasing volumetric change, at the same time ejecting the uidthrough the same passage of the counterbore 158. As previously describedwith reference to the embodiment of Figs. l to 1l, the phases ofincreasing and decreasing volumetric changes continue each for a halfrevolution, minus a diminutive portion of a complete revolutionbetweenphases when a working chamber is completelyl closed, a workingchamber being closed at the time of direction change of volumetricchange from the increasing to the decreasing phase of its cycle, andfrom the decreasing to the increasing phase.

Exteriorly, rotor is contoured to comprise a peripheral surface that iscylindrical on the axis of container 131 which passes through the centerof spheroid 126, and is angularly displaceable relatively into and outof coincidence with the axis of shaft 103, as seen in Figs. l4 and 13respectively. Additionally, the exterior surface of rotor 95 comprisesend surfaces that lie in parallel planes, both of which areperpendicular to the axis of the cylindrical surface 1559-160, thisbeing the axis of the container 131. i

Rotor 95 is contained in shell 162, and rotates interiorly thereof.Shell 162 consists of end plates 163 and 164, with annulus 165 betweenthem, the pieces being assembled and held together by means of bolts166.

Annulus 165 comprises a cylindrical inside surface 167 that ts theperipheral cylinder 159--160 of container 131, and which constitutes abearing in which rotor 9S rotates. The distance between end faces ofannulus 165 corresponds with the length of rotor 95 between outboardfaces of the several outboard panels 132 and 133, and these bear againstrespective inboard faces 168 and 169 of respective plates 163 and 164when rotor 95 rotates inside shell 162.

Actuating arm 115 is secured to annulus 165 by means of cap screws 178,Figs. 13, 14 and l5. When arm 115 is actuated as hereinbefore describedby pistons and 111, to the positions of either Fig. 13 or Fig. 14, shell162 carries Vthe container 131 withfit,` `thecontainer. `rotating on.the surface vof ,spheroid 126 and relative to inboard pane1128.V By this,motiom the angular' relationship between. opposedjfaces V138A` yan'd`129 of the respectiveoutboard` and inboard panels'132 and 128, andopposed faces 130 vand139` of respective inboard and outboard panels 128and i133, is changedjto positions-.0f Figs. '13 and 14 alternatively. i

-Asadditional support, annulus 165 comprises'trunnions 171 and V172.Brackets "173, at the left and right in Figs. 12 and 15, are secured tothefhousing of half members 97.and'9.81by means of cap screws .174, andeach contains a bearing `for theotrunnions '171 and 172 respectively.Shell 162 lrotatesinbearings 175 by the hereinbefore describedactuationof arm 11'5, and spheroid 126 thereby is relieved o'frsomeo'fthebearingload. Brackets v173 seal thehousing o'f'halfmembers`97 and98 at the bearings 175.

Plate 163 of shell 162 comprises the arcuate channels 177 and 1.78on itsinboardface, asV seen in Figs. 17 and 18, and AVsimilar arcuate channels179 and 18,0, Figs. 17 and 21, yareprovided on theinboard face ofplatej164. All the arcuate channels 177, 178,'179 and 180, are on acylinder that iscoincident with the cylinder of the severalcounter-bores 158 and concentric with container l131. Theyiare widekenough to span the counterbores 158, and are in registry therewithVbecause of the vface-to-face bearing relationship betweenfaces of plates163and 164 and panels 132 and 133 respectively.

All the channels'177, 178, 179 and 180 are the same length. In theseveral plates 163 and y164, channels 177 and 179 Vrespectively areadjacent each other and coex* tensive circumferentially, and respectivechannels 178 and 1,80 similarly are adjacent each other and'coextensive.As described hereinbefore withreference to the embodiment of Figs. l tol1, the engine of Figs. 12 to 22 also is symmetrical on opposite sidesof its center.

In plate' 163, arcuate channels 177 and 1,78 are inlet and outlet portsrespectively. Similarly, in plate164, arcuate channels 179 and 180 areoutlet and inlet ports respectively. In shell 162, inlet ports 177 and180 are diagonally opposite each other for the respective different pumpunits on respective opposite sides Ofjnboard panel 128, and outlet ports178 and 179 similarly are diagonally opposite each other. "The severalpump units are 180 out of phase with each other. I

The'distances between adjacent ends of arcuate ports 177 and -178 ofplate 163 are alike, and are Vthe same as distances between adjacentends. of arcuate ports 179 and 180 of plate 164, which also are alike.The distance between adjacent ends of the ports 177, 178, 179 and 180severally is governed by the diameter of the counterbores 158,3beingslightly less to close a counterbore and its kcompanion working chamberwhen positioned betweenports. 'During rotation of rotor 95, constitutingrotation of container 131 inside the shell 162, a given counterbore 158of panel 32 with reference to plate 163, and the `correspondingcounterbore 158 of panel 133 with reference to plate 164, are open toports 177 and 179 respectively as the counterbores travel along theircoextensive lengths and until they pass beyond their ends, are closeduntil they enter registry with ports 178 andl 18) respectively to whichthey then become open, continue to be open to ports 178 and -180respectively as they travel along their coextensive lengths and untilthey pass beyond their opposite ends-when they become closed,`and thesecounterbores continue to be closed until they again come into registrywith ports 177 and 179 respectively Vand become open thereto.

The time interval when a given counterbore 158 remains closed at aposition between adjacent ends of ports 177 and 178 at each of oppositeends thereof, or between ports 179 and 180 at each of opposite endsthereof, is a diminutive portion of a :complete revolution of rotor )5,rand only long enough to prevent lluid flow through the-.counterboreas vapassage, from the higlrpressure side'of anjoutlet poit 17,8or'179respectively in the two pump units, Vtothe lowQpressure "side ofthe respective inletlports177 and I:180. j, k y

The Itwoainletp'ort'sf177 'and "180' 'of respectivek plates 163 VandA164 areconnected v to each` other .to constitute a' container of iluid"in common, and the two outletports 178 'and`179' of'respective plates163V and 164 also are i connected to each other similarly to constituteajc'ontainer of tluid ink common.

In-one ofits faces as seen in Figs. 17 and 19, annulus 195 comprises anancuate channel 1,81, at one endof which .there isa bore 1182 throughltheannulus from face tof'face. fSirnilarl'y inthe oppositevface, asseen in Figs. 17 and20, annulus1'65 comprises an arcuatechannelk 18'3,at one end of Whichthere'is a bore 184 through the annulus from f ace tolface. `Arcuate channels -1'81and 183 are located Vdiarnetricallyopposite each other in annulus 165, and lie in a cylinder common to both`that is concentric with container 1731, and with the cylinder thereofthat contalns counterbores v158l as also the'a'rcuate ports 177,178,;179and 180 vofplates 163 and l'164,fb1ut the diameter of thecylinder'of arcuate'channels 181'a'nd 183 is somewhat greater. Eacharcuate channel 181 and 183 is long/enough to span vthe distance betweenad? 'jacent ends of arcuate ports 177 and 178 in the case of channel181, and in ythe'caseof channel 183 the arcuate ports 179 and 180 ofplate V164.

As seen in Figs. 17 and -18, the inboard face of plate 163 is providedwith fthe bore 185, which coincidesV with the cylinder of arcuatechannels 181 and 183, and which is connected through its back passage186 with the arcuate port; 177` atl an end thereof. The same face .ofplate 163 is provided with bore 187, alsocoinciding with the cylinder ofarcuate channels 181 and 183, and'which is vconnected with larcuate port178 through its back passage 188. Similarly and as seen in Figs. 17 Yandvv21, the inboard face of plate 164 is provided with the bores 189 and`191 which coincidewith the cylinder of arcuate channels 181 and 183,vand which connect each with an end of respective'arcua'te ports 179 and180 through respective back passages190 and 192 ofrports'189V and 191respectively.

By tracing out the described structureV in Figs.V 17 to 21 inclusive,itwill be seen that inlet port 177, through its back passage 186 andbore 185 connecting with arcuate channel 181 of annulus 165, connectswith the diagonally opposite inlet Lport 180, through its back passage192 and bore 191 connecting with ace-to-face bore 182 of annulus 165.Similarly, otlet port 178 o f-plate 163,"th'rough itsy back passage 18Sand bore 187 connecting with face-to-face boreY 184 of annulus 165,connects withV the diagonallyopposite arcuate port 179 of plate-164, bythe latter being connected with arcuate passage V183 of annulus 165through its back passage 190 and bore 189. 1

Bore 194 in the inboard face of plate 163, Fig. 18, connects ,with inletport 177 at a point aboutl midway of its length Vthroughradially-directed back passage 195.. Similarly, and also in the inboardface of plate 163,V bore 196 connects with outlet portY 178 at a pointabout inidway of itslength through radially-directed back passage 197.In the contacting face of annulus 165, and as seen in Fig.` 19,bore'f198 connects with bore 194 of plate 163, and borel 1991of annulusconnects with-bore 196 of 'platei163.Y Bores 194 and 196 of plate 163,-and respective companion bores 198 and 199 of annulus165, Vare locatedjrdiametrically opposite each other, Vand respectivelyconnect withrespective bores 200 and I201,'whicl are opposite eachV other anddirected radially towards each other in annulus 165, and are located atthe centers of respective trunnions 171 and 172. Bores 200' and 201 areintake andexhaust bores respectively. i i y A pipe connectionA isthreaded nto each of the brackets 173;, which adapt the powerfpumpjt'othe pipe standard of thesystem, and these constitute the intake 202 atthel left in Fig. 15, and the exhaust 2,03l at the right. The intake 202and exhaust 203 connect with the intake an exhaust b ores 200 and 201respectively.

In.,the engine of the embodiment ofSFigs. 12 to 22 operating vas a powerpump, rotor 95 is driven by the drive of shaft 103. Whenthe pressurebehind the pistons 110 and 111 is balanced, byl operation of a valve,not shown, the parts are positioned as seen in Fig; 14. A simple-two-wayvalveissuitable for the purpose, with fo v" and' on positions, the valvebeing in off position for the adjustment of Fig. 14. l

Opposed faces 138 and 129 of respective outboard and inboard panels 132and 128, and of respective inboard and outboard panels 128, and 133 theopposed faces 13.0 and 13,9, aredisposed in parallel relationship. Theworking chambers do .not change their volumetric values `by rotor 95being rotated, Aand the pump of the several pump units does not operateto build up pressure. The pump `is out of operation by its valve beingin olf position. f v

When the-valve is turned to on position, a pressure differential issetup behind the several pistons110 and '111, which pressure differentialis high behind piston 111.- Arm, 115 is actuated thereby to the leftfrom its position of Fig. 14 to its position of Fig. 13. This opcratesto` rotate shell 162'in its bearings 175, Fig. 15, carrying with it,container 131 rotating on spheroid 126 in .thesocket of surfaces 136and 137., Outboard panels 132 and 133 are actuated thereby to displacetheir respective faces 138 and 139V angularly'with reference to theirrespective opposed faces 129 and 130 on opposite sides of inboard panel:128, the angles of displacement being the same but oppositely` directed.

In the two pump units at the left and right respectively offinboardpanel 128, working chambers in the phase of increasing :volumetricvalues are.v traveling along the lengths of'` inlet ports 177. and 180as a fluid container in common, respectively of the left and right pumpunits. They yare drawing fluid. into their. cavities successively, eachthrough Vits companion counterbore 158, which is supplied by intake 202through companion bores 198 a'nd'194v respectively of annulus 165 andplate 163, and through radially directed back passage 195 into inletport 177.. f,

The uid that is taken into theV working chambers in the mannerdescribed, is subjected to pressure buildup when the working chambersmove in succession each into its phase of diminishing volumetric values,and their corresponding counterbores 158 then are travelling along thelengths of outlet ports 178 and 179, in the respective pump units at theleft and right. The pressurized uid is poured into the outlet ports 178and 179 as a fluid container in common, from which it is driven through'companion bores-196 and 199 of plate 163 and annulus 165 respectively,and through exhaust port 201, to the exhaust 203, which delivers thefluid to the power system that is serviced by the pump.

The structures disclosed in the drawing present several practicalembodiments of the invention. The scope of the invention is determinedby the accompanying claims.

What is claimed is:

1. In a pressure fluid engine, adjacently located panels with proximatefaces of the adjacent panels spaced apart in opposed relationship andwith the several panel faces being circular on axes of the respectiveadjacent panels intersecting at a predetermined angle, the -panels beingrotatable in unison on their intersecting axes, the engine comprising acontainer peripherally of the panel faces enclosing the space betweenthe opposed faces and comprising three or more radially disposedpartitions extending to the peripheral container and from face to facebetween the opposed panel faces, the partitions being to containvvworking chambers at circumferential intervals between opposed panelfaces, the engine producing pressure variations in the circumferentiallysuccessive working chambers progressively from minimum to maximum and tominimum pressures in response to volumetric changes resulting from theopposed panel faces rotatingv in lunison in the cycle of a revolution, apin coincident, with each partition positioned with its axis ,extendingVradially from the point of intersection between the axes of rotation ofthe several adjacent panels, a bearing for each pin to rotate on itsaxis, each bearing. coinciding with a panel and comprising a seal aroundits pin inhibiting fluid leakagethrough the panel, each pin comprising alengthwise slotvconstituting opposite parallel bearing surfaces, andeachpartition comprising opposite bearing surfaces engaging therespective opposite bearing surfaces `of the slot of its correspondingpin. i

2. In an engine as defined in claim 1, the face of one of said panelsbeing contoured conical on thel axis of rotation of the panel, theconical angle being determined to position opposed faces ,of adjacentpanels closely adjacent to each other and parallel along. a radial planeat the circumferential location of minimum .volume of the workingchambers. l f' i 3. In an engine as defined in claim 1astator and arotor rotatable in the stator, the rotor embodyingthe several adjacentpanels and the working chambers thereof, the stator comprising an intakeand an exhaust,

inlet and outlet ports communicating with'the space between the opposedfaces of adjacentipanels at diametrically opposite intervals inrespective zonesof increasing and decreasing volumes, vand manifoldstructure embodying passages from the intake to the inlet'port and fromthe exhaust to the outlet port.

4.-In an engineas defined in claim 3, each of said adjacent panelscomprising any axiallyy Vdirected shaft,` the stator comprising abearing foreach shaft'and a mechaf nism operable to actuate one of thebearings transversely of the axis of the other shaft to change the anglebetween shafts and theA angular displacement-between the opposed facesofthe panels accordingly.

. 5. lIn an engine as delined in claim 4, -the bearing-actuatingmechanism being adjustable to vary the angular displacement betweenopposed panelfaces progressively from parallel relationshipcorresponding with axial align- Inentof the several shafts'toa maximumangular displacementcorrespondilng withmaximum angular displacementbetween the shafts.

6. In an engine as defined in claim l, a rotor shaft coaxial with one ofthe adjacent panels which is secured thereto rigidly, adjacent mechanismoperable to swing the other adjacent panel on an axis through theintersection of and perpendicular with a plane common to the axes ofboth panels to vary the angle of displacement between the several panelfaces.

7. In an engine as delined in claim 3, of the adjacent panels oneconstituting a pair of outboard panels secured rigidly to each other,coaxially and spaced apart face-toface with their inboard faces deliningplanes that are parallel, and the other of the adjacent panelsconstituting an inboard panel positioned between the outboard panelswith its opposite faces respectively positioned each opposed to theinboard face of that outboard panel on located at intervalscircumferentially of the panel faces from face to face of inboard facesof the several outboard 19 panels, the inboard panel comprising abear/ing for each ofthe several radially directed pins Ylocating theaxis of itspin lin the center-plane of the inboard panel..

' 10. `In' anV engineas defined in claim 9, each partition l1. In anengine as defined in claim 9, each partition consisting of correspondingpartition members in the respective outboard `panels and a correspondingsegment extending continuously between corresponding partition members,each partition member projecting rigidly away from the inboard face ofits outboard panel and comprising an end lface located in a plane commontothe kend faces of all the partition members of the correspondingoutboard panel which is normal tothe axis of the panel',y each segmentcomprising end lfaces at 4its respective opposite ends bearingin'sliding lengagement against the end faces of itsA correspondingpartition members to enable relative circumferential movement betweensegments and their respective Vcorresponding partition members.

I12. Iny an engine as defined in claim 7, each engine unit comprisinganinlet port and an outlet port individualV to itself, a passageVconnecting the intake with the several inlet ports, and a passageconnecting the several' outlet ports with the exhaust. Y

13. In an engine as defined in claim 8, an assembly of theoutboard'panels and the peripheralcontainer enclosing the working(chambers comprising an exterior cylindrical surface coaxial with 'theinboard faces of the outboard panels Vand also exterior flat end facesnormalV to the axis of the cylinder, a shell comprising interiorcylindrical and flat surfaces respectively companion to the exteriorcylindrical surface and end faces of the assembly for bearing engagementtherewith, the rotor comprising 'a shaft and the inhoard panels securedrigidly to each other coaxially and aspheroid secured rigidlyto theinboard panel Yconcentrically with its center-plane, the :rotorcomprising the assembly embodying a spherical bearing surface companionto the spheroidcentered on the axisof its exterior cylindrical vbearingsurface, the stator comprising lbearings for the shaft andmechanism torotate the `shell 'on the center ofthe spheroid on an axis atrightangles 20 to the axis of the shaft bearings to vary the angulardisplacement` between ropposed facesV of the 'ginbaid fand` outboardpanels ofthe rotor. f' V I14. `-In a'nengine l'asgfdefned prisingltrunnionsfon'*anaxisV intersecting the axis the" interior Vcylindricalsurface at right "angles,-N the stator compr-isingl bearings *forl thewtrunnion on anaxis intersectf ing the axis of theshaft bearings Vat,right angles, thlevshell actuating mechanism rotating'the shell on thetrunnion bearings." il

l5. }I n an engine asdefined in claim 13, each,enginel e unitcomprisingan inlet portand an outlet port individual Y to itself, theshell embodying a passage .connecting the several inlet ports andV apassage connecting the vseveral outletfports,v Y i Y l6..I n an engineas defined in claim 13, Atheshell embodying manifold structurecomprising passagesconnecting the intake with the severalinlet ports andpassages connecting theV exhaust with the several outlet ports:

17. In an engine as Ydeiined'in Yclaim 14, .each engine unit comprisingan inlet port and an outlet port individual to itself, the shellembodying manifold structure -cnnprising passages connecting the intakewith the several inlety Vports kand passages connecting the severaloutlet ports Lwith the' exhaust', thejintake and the exhaust beinglocated at the centers ofV the? respective trunnmons ofthe shell. i

18. In an engine as defined in claim 13, the lmechanism for rotatingVthe shell being operable vto two positions alternatively of vparallelrelationship and angular displacement Arespectively between opposed`faces of the several inboard and outboard panels.

i 4,References Citettin the fleof this patent vUNuED STATES .PATENTS15,173 Carpenter June 24, ^1856 865,891 `Heberling et al. Sept. 10, 19072,353,780 Neuland ]lllvy y18, 1944 2,380,886 lvelldie July 3l, `1945V2,525,907 Johnston Oct. 17, 1-950 2,584,426 Crane Feb. 5, 1.9522,678,003 Gerken May 1l, 1954 2,681,046 Barrett June 15, 1954 2,691,348`Gunther -Oct. 12, 1954 2,691,349 Cuny Octal-2, 1954 1 Jonassen` Nov. 18,1958 iaclaimgisgfhe 'sneu clam-

